Portable refrigeration chest



July 27, 1965 K. D. HOLLAND 3,195,631

PORTABLE REFRIGERATION CHEST July 27, 1965 K. n. HOLLAND 3,196,631

PORTABLE REFRIGERATION CHEST 8 Sheets-Sheet 2 Filed June 25, 1962 ulllllBIHLZ July 27, 1965 K. D. HOLLAND 3,196,631

PORTABLE REFRIGERATION CHEST Filed June 25, 1962 8 Sheets-Sheet 3 INVENTOR.

July 27, 1965 K. D. HOLLAND VPORTABLE REFRIGERATION CHEST 8 Sheets-Sheet4 Filed June 25, 1962 July 27, 1965 K. D. HOLLAND PORTABLE REFRIGERATIONCHEST 8 Sheets-Sheet 5 Filed June y25, 1962 July 27 1965 K. D. HOLLAND3,196,631

PRTABLE REFRIGERATION CHEST Filed June 25, 1962 8 sheets-sheet e Alf/i/%JZZ, 7.45%@ Z4@ July 27, 1965 K. D. HOLLAND PORTABLE REFRIGERATIONCHEST 8 Sheets-Sheet '7 Filed June 25. 1962 July 27, 1965 K. D. HOLLANDPoRmsLE REFRIGERATION CHEST Filed June 25, 1962 8 Sheets-Sheet 8 UnitedStates Patent Oce 3,196,631 Patented July 27, 1965 3,196,631 PORTABLEREFRIGERATIN CHEST Kenneth D. Holland, '707 lroortree Road, PacificPalisades, Calif. Filed .lune 25, 1962, Ser. No. 204,989 1 Claim. (Cl.62-238) This invention relates to portable refrigeration chests.

More particularly, it relates torefrigerating systems having a singlecirculating fluid for both power and refrigerating loops. The inventionalso relates to novel apparatus for powering such refrigerationapparatus.

' The conventional campers food chest is normally dependent upon the useof ice to maintain a low temperature within the interior of the chest topreserve foodstuffs over a long period of time. Such chests normally areinsulated on their exterior walls and provide an internal cavity or wellin which a supply of crushed ice is dispose-d. The ice well includes asecondary well in which the chilled food is stored. Such conventionalfood chest are restricted in their capacity depending upon the length oftime the particular food contained therein is to be preserved. lf theindividual using the conventional campers chest contemplates -anovernight or weekend camping trip, then a relatively small amount of icewill maintain the food in a safe condition for the desired period. Onthe other hand, if the conventional chest is required to preserve foodover a long period of time, then the greater amount of ice is requiredand the actual amount of food which may be disposed in the chest isreduced. Further, such conventional ice chests are heavy and aredifficult to transport because of the large amounts of ice which arerequired. Another disadvantage of the conventional campers chest is thatas the ice melts, the water produced thereby is retained in the chestand can, in many instances, damage the food which it is sought topreserve by the use of such chest.

In order to avoid the undesirable characteristics of the conventionalchest, recent developments in campers equipment include a food storagechest wherein a refrigerated brine or coolant-lled insert is disposedinteriorly of the insulated walls of the chest. These brine containersare prefrozen and inserted into the chest prior to insertion of thefoodstuiis into the chest. The advantage of such removable brinecontainers is that as they thaw, the liuid does not intermix with thefood. Also, a much lower temperature is achieved such that a greaterquantity of food may be stored for a longer period of time.

Both the conventional ice chest and the removable brine container-typechests are subject to the disadvantage that they are limited in thelength of time during which they provide refrigeration of the contentsof the chest. When such chests are to be used over a protracted periodof time, then either ice or a means for refreezing the brine containersmust be available. In many camping expeditions, such availability of iceis restricted.

This invention provides a food storage chest which has its ownrefrigerating system. The refrigerating system is powered by a campfireor the like such that the availability of electrical power is not acondition precedent to successful operation of the chest. The power unitoperating the refrigeration portion of the chest is removable from thechest such that the weight of the chest can be reduced duringtransportation of the device. Furthermore, the removability of the powerunit provides for an and apparatus for refrigeration.

` the bores of the iirst and second pairs of bores.

auxiliary power supply at the camping location since the invention alsocontemplates the provision of an electrical power generator inconjunction with the refrigeration power unit. Such a generator isuseful to power electric lights, radios, electric razors, and the like.

Generally speaking, the invention comprises a refrigeration system usinga single circulating fiuid medium. The uid medium circulates through apower circuit and also through a refrigeration circuit. A portion of theflow path of the circulating medium through the power circuit is incommon with a portion of the How of the circulating medium through therefrigeration circuit.

More specifically, the invention comprises a system The system uses onecirculating fluid medium having a gaseous phase and a liquid phase. Theapparatus of the system includes a rst heat input means for changing aportion of the circulating fluid medium from the liquid phase tothegaseous phase thereof. A second heat input means is provided wherein theremainder of the circulating iiuid medium is changed from the liquidphase to the gaseous phase thereof. A prime mover is provided togetherwith uid medium duct means connecting the `irst input means and theprime mover. A heat dissipating means is provided wherein the fluidmedium is changed from the gaseous phase to the liquid phase. Theapparatus of the invention further includes a gaseous phase compressormeans operated by the prime mover and connected for fiow of the fluidmedium to the outlet of the second heat input means. Additional luidmedium duct means connect the compressor means and the outlet of theprime mover to the heat dissipating means. A pump means operated by theprime mover is provided for circulating the liquid phase of the firstportion of the duid and is connected between the heat dissipating meansand the first heat input means. Moreover, the invention also includes apressure reduction means for the liquid phase of the remainder of theiiuid, the pressure reduction means being connected between the heatdissipating means and the second heat input means. This apparatusprovides fluid flow path common to the power and refrigerating fluidmedium flow paths or loops of the refrigeration system.

In terms of the apparatus provided for practicing the refrigerationsystem, the invention further comprises a modular power unit operable bycompressed gas from the first heat input means. The power unit comprisesa housing deiining a central elongate cavity therein. First and secondpairs of oppositely disposed bores are provided in the housing openingto the cavity and extending to closed ends spaced from the cavity. Abeam member is longitudinally disposed inthe cavity and has connectedthereto a plurality of pistons, each of which extends from the beammember into reciprocal engagement with one of Compressed gas inlet andoutlet ducts communicate with the bores of the first pair at the closedends of the bores. Valving means are provided in these inlet and outletducts for alternating the communication of the first bores between theinlet and outlet ducts such that when one of the bores of the first pairis associated with the inlet duct, the other of the bores of the rstpair is associated with its outlet. The power unit further includesfiuid duct means communicating with the second pair of bores for theintroduction of a fluid to be pumped into and out of these second pairof bores. The apparatus provides for alternating communication of thecompressed gas inlet and outlet ducts with the first pair of bores toreciprocate the beam member laterally of the cavity. This reciprocationof the beam member pumps -fluid introduced into the second pair ofbores.

These and other features and objects of the invention will be moreclearly understood by reference to the following detailed explanationand description of .the invention take in conjunction with theaccompanying drawings, wherein;

FIGURE 1 is a schematic representation of the power loop andrefrigerating loop of the refrigeration system;

FIGURE 2 is an enlarged rear elevational view of the modular power unit;

FIGURE 3 is a cross-sectional elevation of the modular power unit takenalong line III-III of FIGURE 4;

FIGURE 4 is an enlarged cross-sectional plan View of the valvingmechanisms for the bores of the modular power unit taken along lineIV--IV of FIGURE 3;

FIGURE 5 is an enlarged fragmentary elevation of the means fortransferring reciprocal to rotary motion for operation of the valvingmechanism of the power piston element and is taken along line V-V ofFIGURE 2;

FIGURE 6 is an enlarged cross-sectional elevation of a second'preferredembodiment of the invention in illustrating an electrical generator;

FIGURE 7 is a plan vieu/with parts broken away, of the boiler or firstheat input means of the refrigeration apparatus; l

FIGURE 8 is an end elevational view, with parts broken away, of theboiler;

FIGURE 9 is a cross-sectional elevation of the umtary refrigerationchest of this invention;

FIGURE 10 is a schematic representation of the operable portions of thedevice when the modular power unit and its associated apparatus isremoved from the food storage chest for operationv as an electricalgenerator and auxiliary power supply; and

FIGURES 11, 12 and 13 illustrate an alternate embodiment of the powercylinder valve.

l Referring to FIG. l, a schematic representation of the common legfluid iiow scheme between the power loop and the refrigerating loop ofthe apparatus is illustrated. A preferred embodiment of the inventionhas a power iluid medium flow path or loop 12 and a refrigerating loop13 having a common fluid iiow path or leg 14 for a single circulatingfluid medium. The circulating fluid medium has a gaseous phase and aliquid phase, and, as an eX- ample, may be ammonia, Freon in any of itsforms, or any other useful refrigerant fluid. The power loop 12 includesa boiler or heat input means 15 illustrated more completely in FIGS. 7and 8 and described in greater detail below. The boiler 15 is powered byexposure to a fire, such as a campfire or the like, and has an inlet andoutlet. The outlet of the boiler 15'is connected to a duct 16'forcirculation of the gaseous phase of the iiuid medium. Duct 16 extendsfrom the boiler 15 to the inlet of a modular power unit 17. A'pump 18 isalso provided in the power loop 12 and is connected for operation to thevmodular power unit 17. In a preferred form of the invention, the pump18 is a portion of the modular power unit 17. The outlet of pump 18 isconnected by a duct 19 to the inlet of the boiler or generator 15 andconducts a portion of the circulating uid medium in its liquid phasefrom pump 1S to boiler 15. Check valves 20 and 21 are provided upstreamand downstream of pump 18. As illustrated in FIG. 1, the duct 19includes the downstream check valve 21.

In the common How leg 14 between the power and refrigerating power loops12 and 13, respectively, a heat exchanger or condenser 23 is installed.Preferably, condenser 23 comprises a plurality of tubes through whichthe fluid medium passes. The tubes are exposed to ambient air whichcirculates around the tubes to carry off heat released as the fluidcondenses inside the tubes. A

duct 24 extends from the outlet of the modular power unit 17 andcommunicates upstream of the heat exchanger 23 with a duct portion 14Ain the common ow leg 14. A similar duct or piping element 14B isconnected to the outlet of the heat exchanger or condenser 23 andcommunicates with a duct 25, including the upstream check valve 21)which extends to the pump 18.

The refrigerating loop of the circulation system illustrated in FIG. 1includes an expansion device 26 included within the extent of a duct 27extending from common ilow duct 14B to the inlet of an evaporator 28.The evaporator 2S is similar to the conventional refrigerationevaporator and has an outlet to which is connected another duct 29extending to the inlet of a compressor 30. As illustrated in FIG. l, thecompressor 36 has first and second stages 31 and 32, but it is withinthe scope of this invention that the compressor 30 may be a single stagecompressor or may have three or more stages. As illustrated in FIG. 1,the compressor 3@ is operably connected.

to the modular power unit 17. In a preferred form of the invention thecompressor is included Within the housing of the modular power unit 17.To complete the fluid flow circuit of the refrigerating loop, a duct 33extends between the outlet of the compressor 31) to the upstream portion14A of the common flow leg 14.

In the preferred system illustrated inV FIG. 1, both the gaseous and theliquid phases of the -single circulating fluid medium are present. Theboiler or generator 15 serves to change the liquid phase of thecirculating medium into the gaseous phase. This gaseous phase istransported by duct 16 to the power unit 17 for operation of the powerunit. Such operation of the power unit drives the pump 18, thecompressor 36 and a fan 34 which is mounted to the heat exchanger 23 toforce ambient air through the heat exchanger 23 to enhance the operationof the exchanger. The gaseous phase of the circulating fluid mediumintroduced into the power unit 17 is at a high temperature and pressurebut is exhausted from the power unit through duct 24 at reducedtemperatures and pressures. This used portion of the circulating fluidmedium is then introduced into the heat exchanger where it is convertedfrom the gaseous phase to the liquid phase. Simultaneously withintroduction of the gaseous phase from the power unit into the heatexchanger, the compressor 30 discharges the circulating uid medium inits gaseous phase into the upstream portion 14A of common leg 14 forintroduction into heat exchanger 23. This W scheme provides that theportions ofthe gaseous phase introduced from power unit 17 andcompressor 30 are intermixed in the upstream leg 14A; Similarly, in theoutlet or downstream leg 14B from heat exchanger 23, a portion ofthe'liquid phase emerging from the condenser 23 is introduced in theduct 25 for ow to and through pump 18. In pump 18,.the pressure of theliquid phase 1s raised for introduction into generator 15 according tothe process described above. The remainder of the liquid phase of thecirculating medium not passed through pump 18 is passed through duct 27and expansion valve 26 into the evaporator 23. In the evaporator 23 theliquid phase flashes or expands into the gaseous phase and in theprocess absorbs heat from the surroundings of the evaporator. Followingthe expansion of the liquid phase of the circulating medium into thegaseous phase in evaporator 23, the gaseous phase of the remainder ofthe circulating Huid is passed through the compressor Sti prior tointroduction into the upstream portion 14A of common fluid ow leg 14.

The ow of the circulating medium through both the power andrefrigerating loops 12 and 13, respectively, is on a continuous flowbasis. A presentation of a heat balance associated with a particularembodiment of the invention is presented in Table 1. The data of Table lis based upon the use of anhydrous ammonia as the circulating uidmedium.

l-HEAT BALANCE OF FIG. 1`

TABLE Heat Wt. flow Tempera Enthalpy transfer 1b./hr. ture "F. P.s.i.a.B.t.u./ll

B.t.u.lhr.

Boiler 6, 355 12. 19 Inlet to Power Unit 17- 12. 19 251 750 691 Outletof Power Unit 17 12.19 120 250 641 Inlet to Condenser 14. 44 157 250 762Condenser 1 14. 44 Outlet of Condenser. 14. 44 110 247 167 Inlet ofBoiler 12. 19 110 76() 170 Inlet of Evaporator-. 2. 0 31 167 Evaporator2. 25 Outlet of Evaporator 2. 25 0 29 612 Inlet of 2d Stage Compressor2. 25 `184 85 706 Outlet of Compressor 2. 25 415 250 832 1 Fan consumes74 Btu/hr.

Referring to FIGS. 2, 3, and 4, the modular power unit 17 isillustrated. Power unit 17 includes a housing 35 having upper and lowerhalves or portions 36 and 37, respectively. These housing portions havemating surfaces 33 and 39, respectively, between which a gasket material4t) made of Mylar or the like is disposed. A series of through bolts 41,extending through the housing portions 36 and 37, secure the portions 36and 37 and the gasket 46 together.

As illustrated in FIG. 3, each housing portion 36 and 37 has a recessformedtherein adjacent its respective mating surface. These recesses aresuch that when the housing portions 36 and 37 are secured together, the

recesses dene an elongated cavity 42 within the extent of the housing35. The cavity has spaced apart upper and lower walls 43 and 44,respectively. A plurality of bores grouped into pairs of bores 45, 46and 47 are formed in the housing 35. Bores 45A, 46A and 47A extend fromthe upper surface 43 of cavity 42 into the upper housing portion 36 toclosed ends spaced adjacent from the upper surface 4S of the housing 35.Bores 45B, 46B and 47B extend downwardly from the lower surface 44 ofcavity 42 and terminate in closed ends spaced from the underside orbottom 49 of housing 35. In addition to the external surfaces 48 and 49of housing 35, housing also has left and right sidewalls 5t) and 51 (asviewed in FIG. 2) and front and rear walls 52 and 53 defining a cubicalconfiguration of housing 35.

Each of the bores of the pairs 45, 46 and 47 are axially alignedrelative to one another with the axes of the bores being orientedvertically with respect to housing 35. An elongated beam member 54 isdisposed in cavity 42 and is oriented parallel to the elongate extent ofcavity 42. A plurality of pistons, arranged in pairs of pistons 55, 56and 57, are connected to the beam 54. Pistons 55A, 56A and 57A aredisposed on the upper side of beam 54 and cooperate within bores A, 46Aand 47A, respectively. Similarly, pistons 55B, 56B and 57B are disposedon the underside of beam 54 and extend downwardly into cooperation withbores 45B, 46B and 47B, respectively. Since all of the pistons aresubstantially identical, with only the lateral dimensions of each pistonvarying depending upon the dimensions of the cylinder in which thepiston cooperates, only piston 56A will be described in detail.

Piston 56A has an elongated connecting rod portion 53 extending betweenaradially flanged lower end 59 and an integral piston head portion 60.The radially flanged end 59 is disposed adjacent beam 54. The pistonhead portion 60 has a diameter slightly less than the diameter ofcylinder 46A. A peripheral groove 61 is formed in the vertical walls ofpiston 60 and receives an C-ring which functions as a piston ring tomaintain sealing engagement with the walls of cylinder 46A.

A longitudinal hole 63 is formed coaxially through piston 56A from head6) to the end portion 59. A countersunk or recessed well 64 is formed inthe head portion 6) and opens toward the closed end of the cylinder 46A.A similar hole 65 is drilled through the beam 64 with the axis of hole65 being as closefto concentric with the axis of cylinders 46A and 46Bas possible. A tie-rod 66, having a diameter along the major portion ofits length less than the diameter of holes 63 and 65, is provided to tiepistons`56A and 56B to the beam 54. The tie rod 66 has an enlarged head67 which is engaged within well 64 of piston 56A when the rod 66 ispassed through holes 63 of pistons 56A and 56B and hole 65 in beam 54.The lower end of rod 66 has a threaded portion upon which a nut 68 isengaged to secure the pistons to the beam 54. Resilient gaskets aredisposed between the enlarged head 67 and nut 68 and the respectiveVpistons to provide secure seating and engagement between the tie rod 66and the pistons 56. V

A plurality of bearing spheres 69 are mounted between the radiallyflanged portions 59 of each piston and the beam 54. Preferably, thespheres are fabricated of Teflon polytetrafluoroethylene or some otherresilient low-friction material, but it is also Within the scope of theinvention that spheres 69 may be metallic. The spheres 69 nest inrecesses provided in the radially anged portions 59 of pistons 56. Aclearance exists between the diameter of the tie-rod 66 and the walls ofholes 63l such that a small amount of lateral wobble relative to beam 54is allowed between the pistons 56. This is desirable since during themanufacture of the modular power unit 17 (wherein the pistons 55, 56 and57 are all ganged or coupled directly to beam 54) the tolerance limitspermitted during manufacture may become additive. ln such a situationthe pistons would be misaligned with the cylinders and would not beproperly engagable within the cylinders 46 and 47 if the pistons 55 to57 spacing between the axes of the cylinders 45A, 46A and 47A may bedifferent than the spacing between the corresponding pistons SSA, 56Aand 57A as well as between the holes 65 in beam 54 for each pair ofpistons. The

' lateral wobble provided by tie-rods 66 and spheres 69 allows forminute adjustments in the position of the pistons to accommodate fortolerance of build-up during manufacture of the device.

The cylinders 45A and 45B and pistons 55A and 55B comprise the power orprime mover portion of the modular unit 17. The prime mover is a doubleacting reciprocating piston engine. A valve chamber 70 is providedwithin each of the housing portions 36 and 37 between closed ends of therespective cylinders 45A and 45B and the exterior surfaces 4S and 49 ofhousing 35. Since the valve mechanisms for the power pistons 55A and 55Bare substantially identical, only the structure of the valve mechanismfor piston 55AV is illustrated and is discussed in detail. Thisdiscussion and explanation will suffice to explain the structure anoperation of the valve for 71 is a slotted duct having its elongateextent parallel to the axis of the valve cylinder or chamber 70.Compressed gas inlet and outlet ducts 72 and 73, respectively, areprovided from the front surface 52 of housing 35 and extend intocommunication with the Valve chamber 70 at horizontally spaced apartpositions of chamber 70. The ducts 72 and 73 have internally tappedportions adjacent the front wall 52 of housing 35 into which pipefittings or tubing connections are engagable. A rotary valve member 75is positioned within the valve chamber 70 and has a blade portion 76disposed between cylindrical barrel-like end portions 77 and 78. AnO-ring 79 is provided peripherally of the barrel portion 78 and engagesthe side walls of valve chamber 70. An annular recess 80 is provided inthe walls of the valve chamber 70 and a resilient snap-ring or retainer81 is engaged therein to secure the valve 75 within the valverchamber70. The valve 75 is rotatable within the valve chamber 75 and oscillatesangularly between two, blade positions oriented approximately 90 apartfrom one another.

As illustrated in FIGS. 2 and 4, the valve chamber 70 opens to a recess82 provided in the upper rear portion of the housing 35. An elongatedshaft 83 extends from the barrel portion 78 of valve 75 into recess 82.Shaft 83 is disposed coaxially with the valve 75 and has a clevis yoke84 secured to its free end within recess 82. The yoke 84 has a pair ofparallel arms 85 and 86 extending laterally therefrom into recess 82.Each of these arms 85 and 86 has a longitudinally oriented slot 87formed Itherein. Cyclic angular displacement of the valve blade 76through an arc of about 90 is impressed on blade 76 by connection of theshaft 83 to a reciprocating rod 88 having a tang portion 89 disposedbetween the spaced apart arms 85 and 86 of the clevis yoke 84. Theconnection between the tang 89 and the yoke 84 is by a pin 90 passedthrough the tang portion 89 and engaging the slots 87 in the yoke arms85 and 86. Reciprocation of the rod 88 is by connection to a rotatingfly-wheel through apparatus to be described below.

A hole 92 is formed through the upper portion 36 of housing 35 from theupper surface 48 into the cavity 412. Hole 92 accommodates areciprocating rod 93 which is secured to beam 54 by a bolt or set screw94 in the central portion of beam 54. First and second enlarged diameterannular portions 95 and 96 are formed in the housing portion 36 adjacentthe housing upper surface 48. An O-ring 97 is secured in an annulargroove 98 of shaft 93 to seal shaft 93 tothe confines of the hole 92 andto serve as a bearing for shaft 93.

As illustrated in FIGS. 3 and 6, a rotatable fly-wheel 100, having a camportion 101 and a gear portion 102, is mounted to the upper surface 48of the housing 35. Fly-wheel 100 has a stub shaft portion 103 extendingfrom its under surface into engagement with the annular recesses 95 and96 of hole 92 (see FIG. 6). A journal bearing 104 is provided in thesmaller diameter annular portion 95 of hole 92 and engages the lower endof stub shaft 103. Preferably the journal bearing 104 is fabricated fromTeflon plastic, however leaded brass or any other suitable journalbearing material may be used. A spring retainer ring 105 secures athrust bearing collar 106 to the stub shaft 103 within the extent of thelarger annular recess 96. The collar 106 is spanned by a pair of annularthrust bearing rings 107 and 108 also fabricated preferably from Teflonand fixed within the annular recess 96.

Attop plate or bracket 110 is secured to the upper surface 48 of housing35 and has an aperture 111 therein through which the stub shaft 103 offly-wheel 100 extends. Aperture 111 has a Teflon sleeve 112 shrunk intoits extent; the sleeve 112 closely journals the stub shaft 103. Auaperture or hole 113 is drilled radially through the stub shaft 103within the extent of the porl '8 tion bounded by sleeve 112. Hole 113extends into communication with a hole or bore 114 formed axially ofy-wheel 100. The reciprocating shaft 93 secured to the cross-beam member54 reciprocates within the y-wheel bore 114. The upper end of shaft 93has a circumferential groove 115 therein, which, if developedonto aplanar surface, would trace a substantially sinusoidal curve of the typeindicating harmonic motion. The developed prole of groove 115 is suchthat it is the graphic representation of the mathematical transformationfunction between the nature of reciprocation of rod 93 and uniformrotational motion of flywheel 100.

A pair of balls or spheres 116 are engaged within the lateral hole 113of fly-wheel shaft 103. The innermost one of these balls is located soas to span the gap between the fly-wheel 100 and the groove 115 formedin the upper end of the reciprocating shaft 93. Since ily-wheel 100 isfixed from axial movement by the thrust collar 106 engaging the thrustbearings 107 and 108, reciprocatory motion of the shaft 93 istransformed into uniform rotaJ tional motion of the ily-wheel 100 as thesphere 116 engages groove 115. If desired, a pin may be used in place ofballs 116.

It was mentioned earlier in this description of the invention that thevalve associated with the inlet and outlet ducts 72 and 73 of cylinder45A was regulated by the rotation of y-wheel The cam portion 101 offly-wheel 100 has a control camming groove 120 formed around itsperiphery (see FIGS. 2, 3 vand 5). j The groove 120 has a lower portion121 and an upper section 122 joined together by transition portions 123of the groove 120. The control portions 121 and 122 of cam groove 120are parallel to one another and are disposed parallel Ito the uppersurface 48 of housing 35. The reciprocating rod 88 connected to theclevis yoke 84 of power piston valve 75 extends into a recess 125 formedin Athe rear side 53 of housing 36 above the parting line 38. In thevicinity of the recess 125, the reciprocating rod 88 is bent into ahorizontal portion 126 lying transversely of the recess 125. The rod 88is then bent back parallel to itself in a vertical portion 127 whichextends upwardly through the upper housing portion 36 and through thetop plate to terminate in an end portion i 128 adjacent cam portion 101of ily-wheel 100. A laterally extending pin 129 is fixed to theprojecting end 128 of rod 88 and extends from rod 88 into engagementwith the camming control groove 120 in fly-wheel 100. Rotary motion offly-wheel 100 causes the rod 88 to reciprocate as the pin 129 maintainscontact between the sides or walls of groove 120.

Groove 120 has a preselected configuration and is disposed in apredetermined orientation relative to the flywheel 100. This orientationis correlated to the position of groove formed in the upper end ofreciprocatory rod 93. The phase relationship between grooves 115 and issuch that as the beam 54 nears one limit of its motion laterally of theelongate extent of cavity 42, the blade 76 of valve 75 is caused to moveabout 90 from the position it maintained just previously to the angulardisplacement of the blade. The exact relationship and method ofoperation of the valving mechanism will be referred to following theexplanation of the ducting for the inlet and outlet of compressed gas tothe power piston cylinders 45A and 45B.

It was mentioned previously that the valving mechanism for the powerpiston cylinder 45B was substantially identical to valve 75 associatedwith the power piston cylinder 45A. The actuation of the valve forcylinder 45B is through the mechanism of a reciprocating rod 130 (seeFIG. 5) and a clevis yoke similar to that illustrated in FIGS. 2 and 4.Rod 130 extends through the upper and lower housing portions 36 into arecess disposed adjacent the end of the valve associated with the lowercylinder 45B. In the case of the lower cylinder 45B, however, the recesscorresponding to recess 82 is disposed on the front side 52 of thehousing 35. Furthermore, the reciprocating rod 130 does not have thereturn bend configuration illustrated with the reciprocatingl rod 88illustrated in FIG. 2. Rather, the rod 130 is straight between its upperend 131 exteriorly of the upper portion of housing 35 and the lowerclevis yoke. The reciprocatory rod 130 associated with the lower powerpiston cylinder 45B is disposed diametrically opposite the rod SSrelative to the axis of rotation of the ily-Wheel 109. Rod 13) isengaged with the controlrcamming groove 120 in ily-wheel 11i by means ofa pin 132 extending between the upper end 131 of rod 1341 and theconiiines of groove 126.

Each of the power piston cylinders 45A and 45B has associated therewitha pair of compressd gas ducts. These ducts are the inlet and outletducts 72 and 73, respectively. The piping for these ducts of the lowerpower piston cylinder 45B is illustrated in FIG. 2. A manifold 135 islocated adjacent the right sidewall 51 of the power unit housing 35. Aduct 136 extends from the manifold 135 to theinlet duct 72 associatedwith the lower power piston cylinder 45B. A second duct 137 extends fromthe manifold 135 to the duct 72 leading to the valve chamber 70 of powerpiston cylinder 45A. A second manifold 133 is provided adjacent theleftsidewall t? of housing 35. A duct 139 extends from manifold 133 to theoutlet duct leading to the lower cylinder 45B. A second duct 140 extendsfrom manifold 138 into communication with the passageway 73 formed inhousing member 36 and leading from the valve chamber 70 of cylinder 45A.Having reference to the schematic diagram of FIG.'1, theV first manifold135 is connected to the duct 16 leading from the boiler or first heatinput means 15 in the power loop 12. The second manifold 138 isconnected to the duct 24 communicating with the upstream leg 14A of thecommon flow path 14 existing between the power loop 12 and therefrigerating loop 13.

As was mentioned previously, a suitable circulating fluid medium for usein the refrigerating system of this invention is anhydrous ammonia. Theammonia is changed from its liquid phase to its gaseous phase in theboiler 15. The gaseous phase is provided in duct 16 at an elevated.temperature and pressure. This high energy ammonia is used to operatethe prime move-r pistons 55A and 55B. As illustrated in FIG. 3, theblade 76 of valve 75 for cylinder 45A is disposed in the conditionwhereby the inlet duct 72 is in communication with cylinder 45A. In suchcondition the pis-ton 55A is driven downwardly of the cylinder 45A' tocause the beam 54 to reciprocate transversely of the cavity 42. In viewof the mechanical connection of the pistons to beam 54, as explainedabove, the piston 55B is caused to move downwardly in cylinder 45B andammonia gas, which previously was used'in a power stroke in cylinder45B, is exhausted from the cylinder. In order for the spent ammonia tobe exhausted from cylinder 45B, the blade of the valve associated withcylinder 45B is oriented whereby communication exists between thecylinder 45B and the outlet duct from the cylinder. As the beam 45rcciprocates or moves downwardly of cavity 42 according to the aboveprocess, the y-wheel 1d@ is rotated by interaction between ball 116 andthe groove 115 in reciprocatory shaft 33. During the downstrolre ofpiston 55A, blade 76 is indexed to a dwell position over aperture 71whereby the intaken ammonia expands. As the piston 55A nears thedownward :limit of its travel, the ily-wheel '1110 rotates such that thepin 129 governing reciprocatory motion of rod 88 moves to the upper camgroove portion 122. This movement actuates the Valve member 75 such thatit is vindexed through the remainder of its approximately 90 arc 0fmovement (in a counterclockwise direction as viewed in FIG. 3) and theexhaust or outlet duct 73 is brought into communication with cylinder45A through the slotted aperture 71. Simultaneously, with this indexingof the valve for cylinder 45A, a.90 indexing occurs with the valve forcylinder 45B whereby the outlet duct is closed from communication withcylinder 45B and the inlet duct is engaged. When such reversal of valvecondition occurs, the piston 55B is subjected to the energy of theincoming ammonia` and beam 54 is caused to move upwardly of cavi-ty 4Z.During this process piston 55A expels the spent ammonia present incylinder 45A.

The general schematic diagram of the refrigeration system (FIG. 1)includes a compressor 3i) having a first stage 31 and a second stage 32.In a preferred form of the invention, the compressors 31 and 32 areprovided by the pairs of cylinders 46 and 47 cooperating with thepistons 56 and 57. The pistons 56A and 56B correspond to the first stagecompressor 31; the pistons 57A and 57B correspond .to the second stagecompressor 32. Pistons 56 and 57 are coupled directly and operatively tothe prime mover through the reciprocating beam 54. The valvingmechanisms for the cylinders 46A, 46B, 47A and 47B are substantiallyidentical and therefore only the valving mechanism for cylinder 46A willbe described in detail. This description will suice to describe thestructure and operation of the valves for the remaining compressorcylinders.

In general terms each compressor cylinder comprises a reciprocatingpiston fluid pump. The valve mechanism for such a fluid pump is operatedby the uid pump by the reciprocating motion of the piston. Each pump hasa cylinder bore in a pump housing; the bore being closed at one end. Thepump housing has first and second cavities therein spaced from theclosed end of the cylinder bore; The housing further defines duc-t meansextending from the cylinder bore to each of the cavities; such ductmeans may be referred to as the cylinder duct means. There may be one ormore ducts in the cylinder duct means. A iiuid inlet duct communicatesexteriorly of the pump housing to the first cavity adjacent thecommunication of the iirst cavity with the cylinder duct means. A iiuidoutlet duct communicates from exteriorly of the pump to the secondcavity adjacent the communication of the second cavity with the cylinderduct means. A valve plug is disposed in each of the cavities forreciprocating motion longitudinally of the cavity. Continuously openauxiliary passage means are provided in the housing from the cylinderbore to each cavity and from the second cavity to the outlet duct. Thepressures developed in the cylinder bore are reflected in the cavitiesto induce reciprocation of the valve plugs for alternating communicationbetween the inlet and outlet ducts and the cylinder bore.

Referring to FIG. 4, a recess 143 is provided in the housing right endwall 51 adjacent the upper or closed end of the cylinder 46A of the rststage compressor 31. A pair of horizontally oriented parallel bores 144and 145 are formed in housing 35 from the inner end of the cavity orrecess 143. These bores 144 and 145 are spaced apartfrom one anothertransversely of the housing 35. The bore 144 extends farther inwardlyfrom recess 143 than does bore 145. A plug 146 is xedly disposed in bore144 adjacent the recess 143. A similar but shorter plug 147 is iixedlydisposed in the outer end of the bore 145. Neither of the plugs 146 and147 extends the full length of the respective bore; accordingly, acavity is defined in the inner end of each of the bores 144 and 145. Aretaining plug 148 is secured in the inner end of the recess 143 by aspring retainer clip 149 engaged in an annular recess or groove 150intermediate the ends of the recess 1413. An O-ring 151 is providedbetween the inner end of plug 148 and the recess 143 to assure that theuid pumped in cylinder 46A will not leak from the housing 35. Y

A duct 153 is provided from the cylinder 46A into communication with thecavities provided by bores 144 and 145. As illustrated in FIG. 4, theduct 153 is coaxial of the cylinder 46A and extends from the closed endof the cylinder. The cavity deiined by the bore 144 is designated ascavity 154, while the cavity provided by bore 145 is designated ascavity 155, While the cavity provided by bore 145 is designated ascavity 155. Each of the cavities 154 and 155 is divided into lirst andsecond length portions of equal diameter. The first and second lengthportions of each cavity are of equal length. As illustrated in FIG. 4the diameters of the cavities 154 and 155 are equal and the totallengths rof these cavities are equal. It is within the scope of thisinvention, however, that the diameters of cavities 154 and 155 may bediierent and that the total lengths of these cavities may be different.It is also within the scope of this invention that the geometricalorientation of the cavities `154 and 155 relative to the duct 153communicating with the cylinder 46A may vary from the coplanar parallelorientation illustrated in FIGS. 3 and 4. To facilitate description ofthe valving apparatus for cylinder 46A, the right ends of the cavities154 and 155 are referred to as the iirst lengths of these cavities whilethe inner or left-hand half lengths of the cavities are referred to asthe second lengths of the respective cavities. 'Ihe cylinder duct 153opens to the first length of the first cavity 154 and to the secondlength of the second cavity 155.

A pumped iluid inlet duct 157 communicates from the exterior of the pumphousing to the cavity 154 adjacent the location at which the cavity 154communicates with the cylinder duct 153. Similarly, a pumped fluidoutlet du-ct 158 communicates from exteriorly of the pump housing 35 tothe second cavity 155 adjacent the location where the cavity 155communicates with the cylinder duct 153. In other words, the pumpedrfluid inlet duct 157 and the cylinder duct 153 open to the rst lengthof cavity 154, and the pumped fluid outlet duct 158 and the cylinderduct 153 open to the second length of the cavity 155. The opening of theinlet duct 157 into cavity 154 extends to the outer or right Vend of thecavity 154. The portions of the inlet and outlet ducts 157 and 158adjacent the exterior sides 52 and 53, respectively, of the housing 35are tapped internally to accommodate suitable piping `fittings wherebytubing or piping for circulating the pump iluid may be connected to thepump housing 35. As illustrated, the inlet and outlet ducts 157 and 158`and the upper end of the cylinder duct 153 are disposed along a commonline transversely of the housing 35.

A valve plug is movably disposed in each of the cavities 154 and 155. Asillustrated in FIG. 4, plug 159 is disposed in cavity 154 and plug 160is disposed in cavity 155. Preferably, the plugs 159 and 160 have alength equal to one-half the total length of the respective cavities.

A pair o'f continuously open auxiliary passageways open from the closedend of cylinder 46A into the second lengths of each of the cavities 154and 155. As illustrated in FIG. 4, a pair of `auxiliary passageways 161open from cylinder 46A into the left end of cavity 154. One Vof thepassageways 161 opens adjacent the extreme inner end of cavity 154. Thepassageways 161 are of considerably smaller diameter than the diameterof cylinder duct 153. Auxiliary passageway 162 opens from cylinder 46Ato the left end of the cavity 155. An additional auxiliary or venturipassage 163 communicates between the extreme right end of cavity 155 andthe pump iiuid outlet duct 158. The Venturi duct 163 is disposed at anangle relative to the outlet duct 158. and is oriented so as to beinclined toward the direction of iow of the pumped uid through duct 158.Duct 163 has a diameter considerably smaller than outlet duct 158.Auxiliary passages 161, 162, and 163 are not Huid iiow ducts but ratherare pressure equalizing passages.

It Was mentioned above that the valving mechanism for each of thecylinders 46A and 46B, 47A and 47B operate in response to the ow offluid passing through the ducts 157 and 158. In order for this featureto be accomplished, the diameterof the reciprocatory plugs 159 and 160dissans posed in cavities 154 and 155 must be suiciently less than thediameter of the respective cavities so as to slide easily between therst and second lengths of each of these cavities. In FIG. 3 the positionof the plugs 159 and 160 corresponds to the positions they obtain duringinlet of the uid to the pump cylinder 46A.

It is assumed that the piston 56A is moving downwardly of the closed endof cylinder 46A; this corresponds to a or pumping stroke. The initialcompression stroke of piston 56A generates an increased pressure incylinder 46A. a reduced pressure is manifested in the cylinder 46A. Thisreduced pressure is reilected in the second or lefthand lengths of thecavities 154 and 155. In response to this reduced pressure, the plugs159 and 160 move to their left-hand positions illustrated in FIG. 3whereby the auxiliary passageways 161 and 162 are closed by the plugs159 and 160, respectively. The chamfered ends of the plugs 159 and 160,and the orientation of the auxiliary passageways 161 and 162 relative tocavities 154 and 155, assures that plugs 159 and 160 move to the extremeleft or inner ends of their respective cavities. As the plug 159 movesto the left end of cavity 154, the inlet duct 157 is exposed tothecylinder duct 153 across the rst or right-hand length of cavity 154 sothat the fluid to be pumped is introduced into cylinder 46A. At the sametime that plug 159 moves to the left-hand portion or second length ofcavity 154, plug 160 assumes the same relative position in cavity byvirtue lof the reduced pressure manifested in the left-hand end ofcavity 155 through the auxiliary passages 162. In this position plugcloses the cylinder duct 153 from communication with cavity 155 and,accordingly, from communication with the outlet duct 158.

Next, let it be assumed that the piston 56A reaches the lower point ofits reciprocatory motion in cylinder 46A and begins to move upwardlyduring a compression or pumping stroke. The initial compression strokeof piston 56A generates an increased pressure in cylinder 46A. Thispressure is reflected in the left-hand portions or second lengths of thecavities 154 and 155. This is possible because of the chamfered ends ofplugs 159 and 160 and because of the orientation of the passages 161 and162. The manifestation of the increased pressure in cylinder 46A throughthe passage 162 at the chamfered end of plug 160 induces plug 160 tomove into the first length or right-hand portion of cavity 155. As thismotion occurs, the cylinder duct 153 is exposed to cavity 155 and to theoutlet duct 158. As this communication is accomplished, fluid pumped incylinder 46A is discharged through the -outlet duct 158. As the pumpedHuid begins to flow through duct 158 a'venturi eect is manifested withrespect to the angled auxiliary passageway 163. In other words, areduced pressure is manifested in duct 163 according to the venturiprinciple of Huid flow mechanics. This reduced pressure in duct 163 isin turn manifested at the right end or first length of the cavity 155further inducing plug 160 to 'continue its reciprocatory motion to aposition adjacent the lixed plug 147. Simultaneously with such motion ofplug 160, plug 161 is induced to move to the first length or right-handportion of cavity 154 by virtue of the increased pressure manifested atthe left end of cavity 154 through passageways 161. Such motion of plug159 closes cylinder duct 153 from communication with the inlet passage157. If there were no motion of the plug 159, the discharge fromcylinder 46A during a compression stroke would be outwardly from thehousing 35 through the inlet duct 157.

The dynamically operated valving mechanism for the compressor cylinders46A, 46B, 47A and 47B provides a compact and effective means forregulating the ilow of the fluid pumped by the pistons in the respectivecylinders. Such a valving mechanism does not require any mechanicallinkages to the moving parts of the iiuid pump or to any auxiliarytiming mechanism. In a preferred form of the invention the reciprocatingplugs 159 and 160 are 1 3 fabricated of Teon Such a material has anextremely `low coefficient of friction such that fine tolerances arepermitted between the plugs and the limits of the cavities in which theyreciprocate, and also such a material is resistant to corrosive actionby the material being pumped in the respective cylinders.

Since the valves for the inlet and outlet of each compressor cylinderare operated by the uid pumped rather than by moving mechanical links,there is no mechanical loss from the friction associated with suchsliding parts. The compressor 30, and the entire modular power unit 17,is thus a more efficient and longer lasting apparatus than if mechanicalvalves were provided. Also, the selfcontained nature of the valveapparatus described as- Sures that the anhydrous ammonia compressed incylinders 46A, 46B, 47A and 47B will not leak from the com pressor. Thisis an important feature when the circulating medium is toxic, has `anoverwhelming odor, or is flammable.

As mentioned above, the valving mechanism for the remaining cylinders46B, 47A and 47B of the two stage compressor 30 of the refrigerationapparatus illustrated in FIG. 1 is similar to that described inconjunction with cylinder 46A. Cylinder 47A has a pumped fluid inletduct 164 and a pumped fluid outlet duct 165. The ow of the fluid in theinlet and outlet ducts associatedwith the first stage compressorcylinder46A is from the front surface 52 to the rear surface 53 of the housing35; the flow through the ducts 164 and 165 of cylinder 47A is in thereverse order.y Accordingly, multi-staging of the cylinders 46A and 47Ais accomplished by connecting a duct or tubing 1'66 between the outletduct 158 of cylinder 46A to the inlet duct 164 of cylinder 47A (see FIG.2).

Since the pistons in cylinders 46A and 47A move in phase with oneanother, both cylinders 46A and 47A experience suction or compressionstrokes at the same time. However, the presence of the cylinders 46B and47B provide for a pump or compressor apparatus wherein the suction orcompression strokes are out of phase with the aforementioned cylinders.Such a configuration, i.e., a two-stage compressor wherein each stagehas two cylinders with the pistons in each cylinderV being 180 out ofphase with the other, provides for a compressor having a smoothdischarge. The discharge from the compressor thus is more free frompulsations and vibrations associated with a single-stage compressor.Such a compressor is referred to as a double-acting compressor.

The ducting associated with the multi-stage compressor 31 of thisinvention is illustrated in part in FIG. 2. A suction manifold 167 isprovided adjacent the sidewall 51 of housing 35 below the compressed gasmanifold 135 associated with the prime mover cylinders 45A and 45B.Branch ducts 168 and 169 extend from the inlet or suction manifold 167to the inlet ducts 157 associated with the first stage compressorcylinders 46A and 46B. Similarly, a discharge manifold 170 is providedadjacent the opposite sidewall 50of` housing 35 below the dischargemanifold associated with prime mover cylinders 45A and 45B. Branch ducts171 and 172 extend from the discharge manifold 170 to the outlet ducts165 of the second stage compressor cylinders 47A and 47B. In thepreferred embodiment of the invention, represented by the schematicvdiagram of FIG. 1, the suction maniv fold 167 for compressor 30 isconnected to duct 29 which extends from the outlet of the refrigeratorevaporator 28. The discharge manifold 170 is connected to duct 33 whichjoins the discharge duct 24 from the discharge manifold 138 of the primemover 17. Ducts 24 and 33, as mentioned above, combine into the upstreamleg 14A of the common iiuid` flow leg 14 of the system illustrated inFIG. 1.

The manifold 166 connected between cylinders 46A and 47A serves as anaccumulator for the discharge of the fiuid in cylinder 46A prior tointroduction of the fluid into cylinder 47A since the pistons 56A and57A are in phase. If it is desired that the first stage pump cylindersdischarge directly to the second stage cylinders, then ducting isprovided between the outlet of cylinder 46A and the inlet of cylinder47B. Similar ducting is provided between the cylinders 46B and 47A. Sucha ducting system, however, may be more voluminous than the systemillustrated although the pressure head loss and the over-all eiciency ofthe compressor will be increased. The accumulator feature of duct 166 isuseful only when the fluid pumped is a compressible fiuid; such is thecase with the refrigeration system shown in FIG. 1.

While it is within the scope of this invention that the compressor 30 bemounted in a housing completely separate from the housing for the primemover 17, the ganging together of the pistons 55-57 of the prime moverand the compressor provides an extremely compact modular power unithaving utility in al self-contained portable refrigerating chest asprovided by this invention.

The refrigeration system illustrated in FIG. 1 includes a pump 18 forthat portion of Vthe fluid medium which circulates through the powerloop 12. As illustrated, pump 18 is mechanically directly connected tothe power unit 17. In a preferred form of the invention, the pump 18 isincluded within the housing of the power unit 17 in a manner similarv tothe inclusion of the rst and second stage compressors 31 and 32 in thehousing of the power unit 17.

Referring to FIG. 3, a pump cylinder is formed in the lower portion 37of the power unit housing 35. The axis of the pump cylinder 175 isparallel to the direction of reciprocation of the gang beam 54 and, asillustrated, is concentric to the axis of the bore 92 wherein the rod 93reciprocates. A pump piston 176 is disposed in cylinder 175 and isconnected to the gang beam 54 by a connecting rod 177. A preferred formof the invention provides that the connecting rod 177 is an integralportion and extension of the reciprocating rod 93. A piston ring 178, inthe form of an O-ring, is mounted peripherally of the piston 176 toprovide sealing engagement with the vertical walls of 'the pump cylinder175. A single pumped uid inlet and outlet duct 179 is provided throughthe housing portion 37 from the lower surface of the housing 35 intocommunicati-on with cylinder 175. The lowermost portion of the duct 179is internally threaded to accommodate a pipe fitting whereby ductingexternally of housing 35 may be connected into fluid flow relation withcylinder 175. Suitable check valve mechanisms 20 and 21 (notillustrated) are provided inthe ducting externally of housing 35 tofacilitate the use of a single duct communicating with the cylinder1.75,. It is Within the scope of this invention, however, that a pair ofducts for inlet` and outlet of pumped fluid to the pump chamber 175 maybe provided, and that each of these ducts have a suitable check valveassociated therewith.

A portable refrigerator chest 180 provided by this invention isillustrated in FIG. 9. Generally speaking, the refrigerated chest 80comprises an upwardly open shell, a lid, and means connected to theshell for engaging the lid in closure relation with the shell. Apartition is provided transversely of the shell to vdefine first andsecond portions of the shell. Insulation means are disposed in the firstshell portion and define a cavity opening upwardly of the first shellportion. A liner member configured generally to the shape of the cavityis disposed in the cavity in spaced apart relation from the insulation;the liner member opens upwardly of the cavity. Liner mounting means areconnected from the liner member to the shell and to the partition formounting the liner in the cavity in spaced apart relation to theinsulation. A refrigerant lfluid is provided in the cavity between theliner member and `the insulation. A coolant fluid circuarsenal latingmeans is disposed in the cavity between theinsulation and the linermember. Insulation is disposed in the lid so as to be inoverlyingrelation to the shell first portion when the lid is in closurerelation with the shell. Further, the chest includes means in the shellsecond portion for chilling coolant fluid and for circulating chilledcoolant fluid through the coolant circulating means to freeze therefrigerant fluid.

The chest 180 includes a shell-like lower portion 181 and a lid 182.Preferably the lid is hinged to the lower portion 181 by hinge and latchmeans (not shown) which are well-known to those skilledY in the art offabricating insulated containers. The shell 181 has end Walls 183 and184, a bottom wall 185, and front and rear walls which are notillustrated. A partition 186 is provided parallel to the end walls 183and 184 to divide the lower portion of the chest 180 into a firstportion 187 and a second portion 188. As illustrated in FIG. 9, thefirst portion of the chest occupies -the major volume within the shell181. Partition 186 extends between the forward and rear walls andbetween the bottom 185 and the upper limit of the lower shell 181.

A solid insulation material 190 lines theinterior Walls of the shellfirst portion 187. This insulation 190 has a thickness, relative to theboundaries of the first shell portion 187, of approximately 1% inches ina preferred embodiment of thisinvention. The insulation 190 defines acavity opening upwardly :of the shell 181. A suitable insulationmaterial is expanded polystyrene or polyurethane foam. Y

A liquid impervious membrane 191V covers theinterior surfaces tof theinsulation 190 defining the upwardly open cavity. This membrane may bealuminumfoil or may be a sprayed plastic material which is allowed toharden on the surface of the insulation 190. f v

A liner orwell member 193, configured generally to the configuration Vofthe cavity defined by insulation 190, is positioned Within the cavityand opens upwardly of the shell 181. -The dimensions of the liner 193are less than the dimensions of the cavity as defined by the liquidimpervious membrane 191. Accordingly, a space isprovided between theexterior sides of the liner 193 and the liquid impervious membrane 191.In a preferred form of the invention such a clearance is on the order ofs/s inch. A peripheral ange 194 is provided around the upper exterioredge of the liner 193. Flange 194 is connected to the upper extent ofthe shell first portion 187 at the parting line 195 between the shell181 and lid 182. An effective method of securing flange 194 to shell 181is by welding. As illustrated in FIG. 9, the liquid impervious membrane191 extends lalong the underside of flange r94 to theinner walls ofshell 181 to provide for complete liquid sealing. of the insulationmaterial 190.

A refrigerant fluid 197, such as a brine or the like, is disposed in thespace between the liquid impervious membrane 191 and the liner member193. Preferably, the uid provided in this chamber is not freezable andis stable in the range of operating temperatures (-l0 F.7to 100 F.)encountered in the device. `A coolant circulation coil 198 is disposedin the chest between liner 193 and the membrane 191. The coil 198 is inthe form of a continuous length of tubing which is coiled into abasket-shape .to accommodate the liner member 193. The tubing 198 is inintimate contact with the refrigerant fluid 197. The coil 198 comprisesthe evaporator 28 illustrated in the schematic diagram of FIG. 1.Suitable inlet and outlet ducting (not shown) to and from the evaporator28 is provided through the insulation .190 and through partition 186into the second portion 188 of the chest 180 forconnection to theapparatus mounted in portion 188 and to be described below.

The lid 182 preferably is of aAdish-shaped configuration which isconcave downwardly. A partition1919 is provided in lid 182 and extendsbetween the front and rear walls of the klid in alignment with the shellpartition 186.

The portion of the lid 182 overlying the shell first yportion 187contains an insulation material 200, preferably of the type used in theshell first portion 187. An extruded .gasket retainer 201 is mounted tothe inner extent of the lid around the' periphery of the first-portionand mounts a resilient gasket 202. The gasket 202 is engageable with thefiange 194 of the well or liner 193 when the lid 182 is in closurerelation with the shell 181. In a preferred form of the invention, theinsulation 200 in lid 182`is completely hermetically sealed by a plate203 which is secured to theinner extent of the gasket molding 201.Preferably plate 203 is a piece of sheet aluminum and serves to assurethat moisture does not enter into the lid insulation 200.

The second portion 188 of the chest shell 181 is uninsulated. A seriesof louvres or air circulation vents 205 are provided in the wall 184 ofthe chest adjacent the bottom 185. A similar set of louvres or airventsr206 is provided in the upper portion of the lid 182 above theshell second portion 188. The modular power unit 17 described above ismounted in the lower portion of the shell second portion 188. ThecondenserV 23 is mounted above the modular power unit by a series ofbrackets 207 connected to the partition 186. p

As illustrated in FIG, 9, a fan 34 is mounted to the modular power unit17 'adjacent the underside of lthe condenser 23 to provide a forceddraft of ambient air upwardly past the tubes of condenser 23 throughwhich the gaseous .phase of the circulating medium circulates forcondensation therein.l The gaseous phase of the circulating medium isprovided from the Ioutlets of the power unit power cylinders 45A and 45Band from the compressor 30.

Fan 34 is mounted to the modular power unit housing 35 in a mannerillustrated in FIG. 3. It was mentioned above that the fly-wheel has agear portion 102 about its lower periphery. Gear .102 engages a gear 218which is secured to a fan shaft 211 journaled into a recess 212 in theupper portion of the housing 35. A journal bearing 213 is disposed inthe recess or well 212 and engages the lower. end of the fan shaft 211.A radial collar 214 is provided on the shaft 211 and is positioned onshaft 211 such that the upper surface of collar 214 is substantiallycoplanar with the upper surface 48 of housing 35. An aperture 215 isformed through the top plate to accommodate the shaft 211. A thrustbearing 216 is provided in the underside of the top plate 110peripherally of hole 215 and engages the upper surface of the shaftcollar 214. The under surface of the collar 214 engages the upper end ofthe journal bearing 213. A fanrotor 217 is secured to the upper end offanV shaft 211. Rotational motion of the ily-wheel 100 rotates the fanshaft 211 through interaction between the gears 102 and 210.

Suitable ducting, such as pipe or tubing 219 connected to theinlet-outlet duct 179 of the liquid pump 18, is provided from the powerunit housing 35 to the condenser 23.-

The inlet and outlet ducts to and from the evaporator coil 28 areconnected to the condenserrand to the suction manifold of thecompressor, respectively, according to the schematic illustration ofFIG. 1. It is considered'that such auxiliary piping and ductingconnections between the elements of the refrigerator chestdescribedabove are within the talents of one skilled in the manufactureof refrigeration systems and therefore such auxiliary ducting is notillustrated.

As mentioned above, the boiler for the anhydrous ammonia circulationmedium is adapted for use in conjunction with a campfire or any otherheat source such as gas, gasoline, or kerosene combustion unit. Such afeature provides a refrigerator chest 180 which is extremely useful oncamping trips. FIGS. 7 and 8 illustrate a preferred embodiment of theboiler 15. The boiler 15 comprises a coiled length of metal tubing 220.The tubing has opposite ends 221 and 222 to which are attached pipefittings 223 and 224.,l The end 221 of the tubing is the inlet end ofthe coil 220 while end 222 corresponds to the outlet of 1 7 the boiler.From the inlet, the tubing 220 is arranged into a series of U-shapedbend portions 226 wherein the straight legs 227 of the bend portions 226extend parallel to one another over the length ofthe boiler 15. Asillustrated in FIG. 7, there are nine convolutions or bend portions 226,the central three of which are arranged in a horizontal section 223 withthe two outer groups of three return bends being arranged in angulardepending sections 229 and 239 having planar configurations oriented atsubstantially 120 relative to the central portion 228 (see FIG. 8).

A yoke member 231 of electrical insulation material bridges the oppositeends 221 and 222 of the coil tube adjacent the pipe fittings 223 and224. A 115 volt, 60 cycle A C. line cord 232 is connected to theinsulating block 231. A resistance wire filament 233 is disposedinternally of the tubing 220 over its length. One conductor 234 of theline cord 232 is connected through the insulator 231 to one end of theelectrical resistance filament 233 and the other line cord conductor 235is connected to the opposite end .of the resistance filament tube 233.

In operation at a camp location, suitable ducting or tubing forconnection of the liquid phase of the circulating medium is connected tothe inlet pipe fitting 223. Preferably, such ducting is connected to thepump .18 in power unit housing 35. A similar ducting or tubing isconnected to the pipe fitting 224 for vconduction of the high energycirculating medium gaseous phase from boiler 15 to the power unit 17.Preferably such ducting is permanently fixed to the boiler 15 with theends of each of these ducts remote from boiler 15 being fitted with aquick disconnect tubing fitting (not shown) adaptable for connection tothe pump 1S and to the inlet of the power unit 17, respectively. Theducting from the boiler 15 and the quick disconnect pipe iittings,preferably similar to the self-sealing quick disconnect fittings used inconjunction with compressed air systems, are not illustrated since theselection of such apparatus is considered to be within the scope of thetalents of one skilled in the art.

The chest 130 is used at a remote location, or campsite,

by connection of the boiler 15 to the pump 18 and the power unit asmentioned above. The boi-ler 15 is placed in or `directly adjacent acampfire. As the uid medium contained within the boiler 15 is heated, itis boiled from the liquid phase to the gaseous phase. The gaseous phaseemerges from the boiler -15 at an elevated temperature and pressure andis introduced to the inlet manifold 135 of the modular power unit 17.This high energy gas operates the power pistons 45A and 45B according tothe method of operation described above. Reciprocation of the beam 54rto which the pump piston i178 is ganged causes the liquid phase of thecirculating medium to be circulated into the boiler 15. Energization ofthe power loop 12 of the refrigeration system also energizes therefrigeration loop by virtue of the common flow leg 14 existing betweenthe power and refrigeration loops 12 and `13 and because of themechanical interconnection between compressor and the power unit 17. Asthe power unit operates according to the procedure described above, theexhausted or spent portion of the gaseous phase passing through thecylinders A and 45B is `passed through the condenser 23 wherein it ischanged Vfrom the gaseous ph-ase to the liquid phase. A portion of thecondensate is passed through the evaporator coils 198 lininggthefoodstuff receiving well 193 in the firs-t portion 187 of the chest 180.Prior to introduction into the coils 1-98, however, the liquid phase ispassed through an expansion valve or capillary tube wherein the pressureof the -liquid phase is materially reduced. In the coils 19S of theevaporator 28, the liquid phase of the anhydrous ammonia circulatingmedium is converted to its gaseous phase.Y The gaseous phase of theammonia -coolant fluid is then passed from the tubing coil 198 into theinlet manifold 167 of compressor "31) for compression Iaccording to the"operation of the apparatus described above. As the liquid phase of thecoolant fluid is evaporated or fiashed into t-he gaseous phase in thecoils `198 of the evaporator 23, heat is extracted from the refrigerantuid -197 until the refrigerant cools to the desired temperature. Afterthe refrigerant cools, the boiler 15 may be removed from the campfire toshut down the power unit. The cooled refrigerant fluid is their reliedupon to `maintain the interior of Well 193 in a refrigerated -or cooledcondition such that perishable foodstuffs may be kept for an extendedperiod of time within the insulated well 193.

As illustrated in FIG. 9, the power unit 17 and condenser 23 are mountedin xed relation to the chest 180. It is within the scope of thisinvention, however, that the power unit 17 and condenser 23 may becontained in its own container separate from the insulated portion 187of the chest 139. In such case the ducting from the evaporator 198includes self-sealing quick disconnect connections adjacent thepartition `136. Such separability of the power unit 17 and condenser 23provides for flexibility of the apparatus according to the featuresdescribed below. FIG. l0 is a schematic representation of thecirculation of the anhydrous ammonia circulating fiiuid when therefrigerant loop is disconnected from the power loop as, for example,when the refrigeration process is not needed in order to maintain a lowtemperature in the food storage well 193.

If the power unit `17 and condenser 23 are removable from the foodstorage portion of the chest, auxiliary features of the invention may beused. It was mentioned in the introduction to this description that thisinvention contemplates the provision of electrical generator. Thisfeature of the invention is illustrated in IFIG. 6.

The reciprocating rod 93 which extends upwardly through housing bore 92lends itself to the provision of an alternating current electricalgenerator. A central portion of the reciprocatingrod 93 is comprised ofa length of permanently magnetizfed metal 249 secured to the adjacentnon-magnetic portions of the rod 93 by bolts or stud portions 241 and242 extending from the non-magnetic portion and engagcable with-inthreaded recesses 243 and 244 provided in opposite ends of the magnet24). An annular recess 245 is provided in the lower por-tion of the bore92 l'adjacent cavity 42 in which the gang beam 54 reciprocates. A coilof electrical conductor wire 246 is disposed in the Iannular 4recess245. Preferably, .as illustrated in KFIG. 6, the coil 246 is embedded ina body of electrical potting material 247. The coil 246 includesconductors (not shown) leading away from coil 246 for connection into anelectrical circuit externally of housing `35.

AAs the rod 93 reciprocates in the bore 92, according to the processfdescribed above, the movement of the perma nent magnet 240 past thecoil 246 generates a voltage in coil 246. Since the motion of the magnet240 is a reciprocating motion, -t-he voltage generated in coil 246 isal1 alternating voltage. `In a preferred form ofthe invention, thelength of the magnet 240 is at least equal to the axial length of coil246 plus the distance rod 93 reciprocates. In such a situation, neitherof the opposite ends of magnet 240 come within the ends of the coil 246.Such a feature assures that the maximum possible voltage obtainable willbe generated as magnet v240 reciprocates relative to coil 246. Therotary shaft 211 associated with fan 34 may also be used to drive arotary electrical generator if the reciprocating generator provided inconjunction with the reciprocating rod 93 is not included in theapparatus of this invention. Such a rotary generator is illustrated at250 in FIG. l0.

The electrical generator illustrated in FIG. 6 is especially useful whenthe apparatus for powering the refrigerator is removable from chest 180.After the refrigerator cycle has been run to refrigerate and freeze therefrigerant fluid 197, the lapparatus may be disconnected from the foodstorage portion 1 87 for powering electric lights during the evening orfor supplying electrical power to any appliance which is desired to beoperated.

In initially loading the `food storage well 193 prior to I@ departure ona camping or picnic trip for example, the electrical heating element 233included within boiler 1S is used since it is not normally the practiceto lhave an open tire burning in a house, particularly in thesummertime. The refrigerator provided by this invention may be operatedindoors by plugging the line cord 232 into a suitable electrical outletto heat the resistance filament 233. The heating effect is sutiicient-to change the circulating fluid medium within boiler from its liquid toits gaseous phase su-ch that the power unit 17 becomes operative. Inthis manner the refrigeration chest 180 may be operated indoors as wellas outdoors in conjunction with a carnpre. When the power unit andcondenser are located in a housing detachable from the food storagechest, the electrical operation of the refrigeration system isparticularly convenient. If t-he food chest is to be used on a shortpicnic or the like, the refrigerant fluid 197 may be frozen byelectrical loperation of boiler 15. The power unit 17 `and condenser 23are then disconnected from the food chest and left at home. This meansthat only the Weight ofthe pre-cooled and loaded food chest need becarried to the picnic site.

The chest 180 of this invention provides =a .self-contained body ofrefrigerant fluid such as brine or the like. This is to be compared withthe removable brine filled inserts which lare provided in devicespresently known. The removable inserts must be removed from adjacent thefood storage area of .the chest for prefreezing in order that the foodstorage area of the chest may be refrigerated. This invention, on theother hand, provides a device wherein a smaller volume of refrigerantmaterial is required. The reduction of the volume of the liquidrefrigerant reduces the weight of the resulting apparatus. Furthermore,it is preferred that the chest of this invention `as well as the powerunit 17, be fabricated from aluminum or magnesium alloy metal .-in orderthat the overaall apparatus be as lightweight las possible.

FIGS. 11, 12 and 13 illustrate an alternate preferred embodiment of thevalve associated with the power piston cylinders 45A and 45B. Since allof these preferred embodiments are identical, only that valve mechanismassociated with the upper power piston cylinder 45A will be described indetail below.

An elongated cylindrical valve chamber 70 is provided in the upperportion of housing and has its axis perpendicular to the rear wall 53 ofthe housing. Inlet and outlet ducts 72 and 73 of the same configurationas described above communicate from the front Wall 52 of housing 35 tothe valve chamber 71B substantially concentric to the axis ofreciprocation of the piston within cylinder 45A. An elongatedcylindrical valve plug 270 is rotatably disposed within the valvechamber 7). The valve '70 is of the barrel type and has a peripheral0-ring 79 engaged in an annular recess to 271 adjacent its forward end.A second O-ring 272 is engaged between the forward end of barrel portionof the valve 270 and a retainer ring Si) is engaged in an annular recessin the wall of the valve chamber 7b adjacent the linkage recess 82. Thelinkage recess 82 is of the general conguration described above inconjunction with FIG. 4.

Instead of a single slot communication between the valve chamber 70 andthe power piston chamber 45A as described in conjunction with FIG. 4, inFIGS. 11, 12 and 13 a pair of intake and exhaust slots are providedbetween cylinder 45A and the valve chamber 70. An inlet slot 273 and anoutlet slot 274 are spaced apart from one another and are disposedparallel to the axis of rotation of the v-alve member 27). The slots 273and 274 communicate between the upper end of the cylinder 45A and thevalve chamber 7i).

As illustrated best in FIG. 13, an inlet valve passage 275 and an outletvalve passage 276 are formed in valve body 270. The inlet passage 27S isformed in the valve body 270 in such a manner that when it forms aconnection between the inlet slot 273 and the inlet duct 72,

20 the outlet valve passage 276 forms no connection with either theoutlet slot 274 or the exhaust duct 73. Similarly, the outlet valvepassage 276 is so positioned in the valve member 270 that when it makescommunication between slot 274 and exhaust duct 73, the inlet valvepassage 275 makes no connection with either the slot 273 or the inletduct 72. The inlet valve passage 275 has an inlet end 277 and an outletend 278. Similarly, the out- -let valve passage 276 has an inlet end 279and an outlet end 233. The inlet end 277 of the inlet valve passage 275and the outlet end 280 ofthe outlet valve passage 276 are disposedsubstantially centrally of the valve member j 27 @i so as to communicatewith the inlet and outlet ducts 72 and 73, respectively. The outlet end278 of the inlet valve passage 275 and the inlet end 279 of the outletvalve passage 276 are spaced apart from one another longitudinally ofthe elongate extent of the valve body 271i at the central portion of thevalve body 270. Also, the valve passage ends 277 and 280 are on theopposite side of the axis of rotation of the valve body 270 from thevalveV passage ends 278 and 279 (see FIGS. 1l, l2 'and 13).

The valve mechanisms illustrated in FIGS. ll, l2 and 13 provide inercontrol over the inlet and exhaust functions than does the valvemechanism illustrated in FIGS. 3 and 4 since less angular displacementof shaft 83 is required to operate the valve. Y

From the foregoing description and explanation of this invention, it isseen that the system and apparatus of this invention provides a uniquerefrigeration device which is compact and versatile. It is noted,however, that the environment of the invention comprising a campers foodstorage chest has been selected by way of example and is not to beconsidered as limiting the scope of the invention.

While the invention has been described above in conjunction with specicapparatus, this has been by way of example and should not be consideredlimiting the scope of this invention.

What is claimed is:

A system for a refrigerating apparatus having power and refrigeratingloops for flow of a single circulating medium having gaseous and liquidphases, each of the power and refrigerating loops having a circulatingmedium flow path common to the other loop, the system compr1smg (a) heatinput means in the power loop for changing the circulating medium fromthe liquid phase to the gaseous phase and having a circulating mediuminlet anda circulating medium outlet,

(b) a power unit in the power loop having a circulating medium inlet andan outlet and connected to the outlet of the power loop heat inputmeans,

(c) a circulating medium pump means in the power loop discharging to theinlet of the power loop heat input means and operatively connected tothe power unit,

(d) a heat exchanger for changing the circulating mediurn from thegaseous phase to the liquid phase having a circulating medium inletconnected in fluid ilow relation to the outlet of the power unit and acirculating medium outlet, the outlet of the heat exchanger beingconnected in luid flow relation to the pump means,

(e) circulating medium liquid phase expansion and evaporatormeans inthe-refrigerating loop for changing the circulating medium from theliquid phase to the gaseous phase connected in fluid flow relation tothe outlet of the heat exchanger, and

(f) a gaseous phase compressor means having an inlet and an outlet inthe refrigerating loop and operatively connected to the power unit, thecompressor means inlet being connected in fluid flow relation to theexpansion and evaporator means, the compressor 21 means outlet beingconnected in fluid ow relation to the inlet of the heat exchanger, (g)the power unit comprising (l) housing defining a central elongate cavitytherein,

(2) rst and second pairs of oppositely disposed bores in the housingextending from .the Cavity to closed ends spaced from the cavity,

(3) a beam member disposed longitudinally of the cavity,

(4) a plurality of pistons connected to the beam member, each of saidpistons extending from the beam member into reciprocal engagement with`one of the bores of the rst and second pairs of bores,

(5) compressed gas inlet and outlet ducts to and from the housingadjacent each -of the ones of the first pair of bores,

said ducts communicating with Ithe bores of the first pair 'at theclosed ends thereof,

the inlet ducts being connected to the outlet of the power loop heatinput means,

(6) valving means in said compressed gas ducts for alternating thecommunication of said rst bores between the compressed gas inlet andoutlet ducts, one of the rst bores communicating with its associatedinlet duct when the other of the rst bores communicates with itsassociated outlet duct,

(7) rst fluid duct means communicating with the second pair of bores andconnected to the outlet of the expansion and evaporator means, and (8)second fluid duct means communicating with the second pair of bores andconnected to the 5 inlet of the heat exchanger,

whereby said alternating communication of the compressed gas inlet andoutlet ducts with the bores of the rst pair reciprocates the beam memberlaterally of the cavity, and whereby the second pair of bores and thepistons therein comprise .the compressor means in the refrigeratingloop.

References Cited bythe Examiner l UNITED STATES PATENTS 1,451,303 4/23Mitchell 23 0-52 2,052,407 8/ 36 King 62-438 2,226,271 12/ 40 Vose62-438 2,444,489 7/48 Baker 62-439 2 2,532,234 11/50 Kimble 62-4572,570,693 /51 Koonz S10-15 2,844,301 7/5 8 Newton 23 0-53 2,909,902 10/5 9 Newton 62--238 2,986,907 6/61 Hoop 62-510 2,991,632 7/61 Rogers62-498 3,006,167 10/61 Lorch 62--438 3,024,374 3/62 Stauder 310--15ROBERT A. OLEARY, Primary Examiner.

EDWARD J. MICHAEL, Examiner.

UNITED STATES PATENT OFFICE CERTIFICATE 0F CORRECTION Patent No.3,196,631 July Z7, 1965 Kenneth D. Holland It is hereby certified thaterror appears in the above numbered patent requiring correction and thatthe sa'id Letters Patent should read as corrected below.

Column I, line 20, for "chest" read chests column 3,

llne 9, for "take" read taken columns 5 and 6, TABLE l, last Column,line 4 thereof, for "762" read M 672 Column 5, line 69, after "O-rng"insert 62 column 9, line ll, for "l0" read 100 column l2, lines 9 andl0, strike out "or pumping stroke. The initial compression stroke ofpiston 56A generates an increased pressure in Cylinder 46A.", and insertinstead suction stroke for the pump or Compressor.

As the plston 56A moves away from the Closed end of Cylinder 46A,

Slgned and sealed this 8th day of February 1966. (SEAL) Attest:

ERNEST W. SWIDER EDWARD I. BRENNER Attesting Officer Commissioner ofPatents

